WO1992000473A1 - Engrenage cycloidal - Google Patents
Engrenage cycloidal Download PDFInfo
- Publication number
- WO1992000473A1 WO1992000473A1 PCT/DE1991/000531 DE9100531W WO9200473A1 WO 1992000473 A1 WO1992000473 A1 WO 1992000473A1 DE 9100531 W DE9100531 W DE 9100531W WO 9200473 A1 WO9200473 A1 WO 9200473A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cycloid
- parameters
- cycloids
- wheel
- cam
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
Definitions
- the invention relates to a transmission gear, in particular planetary gear with the features of preamble 1, as described in particular in DE-PS 24 33 675 and in preferred embodiments in DE-OS 32 06 992, 34 18 866 and 34 31 123.
- DE-PS 24 33 675 to the state of the art DE-PS 4 64 992 and 15 75 003 are called, which for the purpose of the required clearance between the cam and the roller ring has such a modified curve that it with a reduction in the parameters q and r compared to the respective reference cycloid can describe, while the teaching according to DE-PS 24 33 675, in contrast, has a change in the cam ⁇ -cycloid course compared to the associated reference cycloid, which manifests itself in an increase in the parameters q and r.
- DE-PS 24 33 675 discloses for the first time the structure of a cycloid gear according to the mathematically describable curve shape. This is done there using the terms reference cycloids and cam disk cycloids, the cam disk cycloids being measured to ensure the required play between the gear disks by the reference cycloid by means of an enlarged configuration of the parameters q and r.
- the invention has for its object to enable the person skilled in the art without the need to try out and thus, as a rule, repeated cam disk designs for one and the same gear in the direction of optimized engagement of the gear parts, a cycloid gear of the type in question according to the respective To be able to determine operating requirements already in the status of the gearbox design.
- the skilled person is taught to determine an exact numerical value on the basis of a common quality concept of standardized pairings, which, with the additional specification of the maximum pressure angle, leads to the mathematically determined definition of the parameter changes of the parameters of the same name of the reference cycloid .
- the reference cycloid including the angle ⁇ max, is inherent in the gearbox create determined, which result from the required gear ratio and the torque to be transmitted.
- the quality concept of a pairing familiar to the person skilled in the art leads to a clear numerical determination of the pairing value c introduced within the scope of the invention.
- Planetary gears are preferably used, the EPI cam disk cycloids of which are assigned to the planet gear and the reference cycloids of which are assigned to the ring gear.
- the required qualities can be applied both to the actual cam disk cycloid and to the reference cycloid determined by the points of engagement between the cam cycloid and the pin ring.
- a device for producing the above-described transmission gear is also provided, which is characterized in that control measures installed internally in the device ensure that after input of the required operating parameters, only the input of the pairing value c of the desired quality is required.
- FIG. 1 shows a cross section of a transmission gear according to II in Figure 2, as it is based as an example of DE-OS 32 06 992;
- Figure 2 shows a longitudinal section along the line II-II in Figure 1;
- Figure 3 is a schematic sketch for generating a tendril
- FIG. 4 shows a schematic sketch for generating the same flank as in FIG. 3, but with generation by the links r, n and e (z + 1) of the transmission chain 0, C and N;
- FIG. 5 shows a schematic sketch according to the presentation according to FIG.
- the cam disks 13 and 13.1, 13.2, each provided with a closed cycloid train 11 and 11.1, 11.2, are supported via the eccentric bearings 7 and 7.1, 7.2.
- the closed Zyk ⁇ oidzug 11 and 11.1, 11.2 are in engagement with the bolt 16, which are fixed concentrically about the central axis 0-0 in the bolt ring 4.
- Axis of rotation MM or M'-M 'bores 17 and 17.1, 17.2 are arranged in which the rollers 20 mounted on bolts 19 engage, which on one side fit into a bottle 21 of the output shaft 6 and on the other side via clamping rings 30 with pressure pieces 31 and
- Screws 32 in a bottle 21.1 of the output shaft 6 are fixed concentrically about the axis of rotation 0-0.
- the output shaft 6 is 1m bolt ring 4 mounted on the roller bearings 22, 23.
- the bolt ring 4 is in a known manner by Oeckel
- Sealing element 27.1 required.
- the screws 28 attach the two covers 24, 25 and can serve to fix the gear;
- Gearboxes are devices for forming, here speeds and moments.
- a transmission consists of links; one of them must be defined as a frame.
- the joint 0 lies in the central axis 0-0, one of the centers of the bolts 16 of the bolt ring 4 is the joint C; joint N is a double joint and acts as an instantaneous pole.
- the pitch angle between two of the bolts 16 corresponds to the generation angle of ⁇ and et is 360 ° / (z + 1).
- stationary gearboxes also called epicyclic gearboxes
- rotating bolt ring 4 by 0
- rotating cam disks 13 by M-M and 13.1, 13.2 and M'-M
- joints 0 and M are fixed to the frame.
- this stationary gear takes on the function of a planetary gear by changing the frame, for example on the joints 0 and C.
- the lines from the hinge 0 to the center point C of the bolts 16 represent the normals to the cycloids 11 and 11.2, 11.2 in their contact points Q at a distance q each from C with the cam cycloids 13 and 13.1, 13.2 and thus provide the evidence for the gearing law and at the same time for the reference cycloid.
- the same flank as in FIG. 3 can also be generated schematically with the terms r, n and (e + e. Z).
- the frame change from the generation according to FIG. 4 with frame joint M as the center of the cycloid to the sequence according to FIG. 1 and with frame joint 0 as the center of the pin ring can be more easily understood.
- the indices "S" indicate the apex position, "E” the engagement position and "T” the valley position.
- the valley position differs only from the apex position by reversing the direction of the link e. In both positions the gear chain becomes a straight line.
- the angle ⁇ between the links r and n at joint C has the value zero in the apex and valley position and reaches its maximum in the so-called engagement position at the angle value of 90 ° between the links n and e (z + l) at joint N.
- the invention is shown schematically in FIG. 5 for the vertex and engagement position by converting a reference cycloid BZ into a cam disk cycloid GZ by increasing the parameters:
- the point (W of the cam disk cycloid GZ lies on a straight line approximating the ⁇ um range, which is parallel to the term e (z + 1) and divides the triangle Q GE , Q BE , G HE into two further triangles.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
- Friction Gearing (AREA)
- Steroid Compounds (AREA)
Abstract
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE59106955T DE59106955D1 (de) | 1990-06-27 | 1991-06-27 | Zykloidengetriebe. |
EP91911964A EP0535109B1 (fr) | 1990-06-27 | 1991-06-27 | Engrenage cycloidal |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DEP4020504.5 | 1990-06-27 | ||
DE4020504A DE4020504A1 (de) | 1990-06-27 | 1990-06-27 | Zykloidengetriebe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1992000473A1 true WO1992000473A1 (fr) | 1992-01-09 |
Family
ID=6409204
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1991/000531 WO1992000473A1 (fr) | 1990-06-27 | 1991-06-27 | Engrenage cycloidal |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0535109B1 (fr) |
AT (1) | ATE130664T1 (fr) |
DE (2) | DE4020504A1 (fr) |
WO (1) | WO1992000473A1 (fr) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2296751A (en) * | 1995-01-06 | 1996-07-10 | Teijin Seiki Co Ltd | Planetary gear apparatus having epitrochoid teeth with a modified profile |
WO2013004029A1 (fr) * | 2011-07-01 | 2013-01-10 | 重庆大学 | Pignon cycloïde de transmission épicycloïdale basé sur une conjugaison ligne-surface |
CN102889340A (zh) * | 2011-07-17 | 2013-01-23 | 吴小杰 | 大型立式摆线减速器 |
CN102889339A (zh) * | 2011-07-17 | 2013-01-23 | 吴小杰 | 大型卧式摆线减速器 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6168235B1 (en) * | 1998-11-16 | 2001-01-02 | Dura Global Technologies Inc. | Recliner control mechanism for a seat assembly |
DE10123548C5 (de) * | 2000-06-06 | 2012-12-20 | Sew-Eurodrive Gmbh & Co. Kg | Umlaufgetriebe, Baureihe von Umlaufgetrieben und Verwendung eines speziellen Werkstoffes zum Erreichen eines geräuscharmen Betriebs |
DE102004048197A1 (de) * | 2004-09-30 | 2006-04-06 | Robert Bosch Gmbh | Exzentergetriebe |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE464992C (de) * | 1928-09-03 | Friedr Deckel | UEber- oder Untersetzungsgetriebe | |
DE2433675A1 (de) * | 1974-07-12 | 1976-01-15 | Rudolf Braren | Planetengetriebe |
-
1990
- 1990-06-27 DE DE4020504A patent/DE4020504A1/de not_active Withdrawn
-
1991
- 1991-06-27 AT AT91911964T patent/ATE130664T1/de not_active IP Right Cessation
- 1991-06-27 EP EP91911964A patent/EP0535109B1/fr not_active Expired - Lifetime
- 1991-06-27 WO PCT/DE1991/000531 patent/WO1992000473A1/fr active IP Right Grant
- 1991-06-27 DE DE59106955T patent/DE59106955D1/de not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE464992C (de) * | 1928-09-03 | Friedr Deckel | UEber- oder Untersetzungsgetriebe | |
DE2433675A1 (de) * | 1974-07-12 | 1976-01-15 | Rudolf Braren | Planetengetriebe |
Non-Patent Citations (1)
Title |
---|
FEINWERKTECHNIK + MESSTECHNIK. Bd. 88, Nr. 7, November 1980, MüNCHEN, DE Seiten 351 - 355; M.LEHMANN: 'Flankenspiel bei Verzahnungen mit Zykloidenkurvenscheiben ' siehe Seite 351, Absatz 3 - Seite 355, Absatz 8; Abbildungen * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2296751A (en) * | 1995-01-06 | 1996-07-10 | Teijin Seiki Co Ltd | Planetary gear apparatus having epitrochoid teeth with a modified profile |
US5695425A (en) * | 1995-01-06 | 1997-12-09 | Teijin Seiko Co., Ltd. | Outer tooth profile of planetary gear apparatus |
GB2296751B (en) * | 1995-01-06 | 1999-03-24 | Teijin Seiki Co Ltd | Planetary gear apparatus |
WO2013004029A1 (fr) * | 2011-07-01 | 2013-01-10 | 重庆大学 | Pignon cycloïde de transmission épicycloïdale basé sur une conjugaison ligne-surface |
CN102889340A (zh) * | 2011-07-17 | 2013-01-23 | 吴小杰 | 大型立式摆线减速器 |
CN102889339A (zh) * | 2011-07-17 | 2013-01-23 | 吴小杰 | 大型卧式摆线减速器 |
Also Published As
Publication number | Publication date |
---|---|
EP0535109A1 (fr) | 1993-04-07 |
DE4020504A1 (de) | 1992-01-16 |
DE59106955D1 (de) | 1996-01-04 |
EP0535109B1 (fr) | 1995-11-22 |
ATE130664T1 (de) | 1995-12-15 |
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